US4041983A - Pressure controlled swing valve with safety feature - Google Patents

Pressure controlled swing valve with safety feature Download PDF

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Publication number
US4041983A
US4041983A US05/594,392 US59439275A US4041983A US 4041983 A US4041983 A US 4041983A US 59439275 A US59439275 A US 59439275A US 4041983 A US4041983 A US 4041983A
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US
United States
Prior art keywords
motor
valve
pilot
pressure
spool
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/594,392
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English (en)
Inventor
Donald L. Bianchetta
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Inc
Original Assignee
Caterpillar Tractor Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Caterpillar Tractor Co filed Critical Caterpillar Tractor Co
Priority to US05/594,392 priority Critical patent/US4041983A/en
Priority to CA246,361A priority patent/CA1030041A/en
Priority to DE19762617549 priority patent/DE2617549A1/de
Priority to FR7614093A priority patent/FR2317578A1/fr
Priority to BE1007454A priority patent/BE843052A/xx
Priority to JP51071265A priority patent/JPS529123A/ja
Priority to BR7604297A priority patent/BR7604297A/pt
Application granted granted Critical
Publication of US4041983A publication Critical patent/US4041983A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0422—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with manually-operated pilot valves, e.g. joysticks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86485—Line condition change responsive release of valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86606—Common to plural valve motor chambers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor

Definitions

  • the present invention relates to control valves and pertains particularly to an implement control valve having a pressure controlled spool for obtaining precisely controlled variable torque from hydraulic motors.
  • Hydraulically operated implements and machines increasingly use higher rates of hyraulic flow and pressures.
  • Such systems frequently use pressures on the order of 3000 psi to 5000 psi and volumes on the order of 50-100 gallons per minute of flow.
  • Such high flows and pressures can result in very abrupt changes in pressure to the motor and high acceleration of the implements associated with such machines due to the high torque induced in the motor. This is especially a problem with rotary hydraulic motors wherein pilot control means is used for shifting the main control valves.
  • pilot control means is used for shifting the main control valves.
  • Such high torque and the changes therein can cause starting and stopping as well as running away of the motor which can damage the machine as well as be uncomfortable for an operator.
  • Pilot operation of control valves for operation of hydraulic implements is normally employed in the prior art for remote operation as well as to reduce the effort required in movement of the controls to thereby reduce operator fatigue.
  • Such prior art systems normally have the disadvantage of a lack of precise control over positioning in relation to motor load or torque of the main control valve.
  • the main control valve spool in such prior art systems is normally provided with rather stiff mechanical centering spring means in order to overcome the forces acting on the valve in order to shift the valve to a non-activating position.
  • higher pressure pilot systems are required in order to shift the valves in the high pressure systems.
  • centering spring pressure in such systems also tends to vary with displacement of the spool. This results in a non-linear relationship between the position of the control lever and the main control valve.
  • a pilot operated motor control valve which is provided constant force centering means and with motor pressure responsive means for providing two of the controlling functions for controlling the pilot shifting of the control valve from its neutral position to a fluid directing position.
  • the controlling means includes piston means responsive to motor operating pressure for acting in opposition to independent and constant pilot pressure that normally shift the valve.
  • the pistons which act in opposition to the pilot pressure are provided with communication of operating fluid from the motor ports of the system so that the opposition to the shifting of the valve is in proportion to the pressure and/or the load on the system for maintaining a constant torque on the motor for a given control lever position.
  • Another object of the present invention is to provide constant torque control means for a hydraulic motor.
  • a further object of the present invention is to provide a pressure controlled pilot operated control valve with controlling means that controls pilot shifting of the valve as a function of the load on the system and in relation to the control selector position.
  • FIG. 1 is a schematic layout partially in section, of a system embodying the present invention
  • FIG. 2 is a sectional view taken generally along lines II--II of FIG. 1;
  • FIG. 3 is a graphic illustration of motor torque plotted vertically against control lever travel for the present system.
  • FIG. 1 there is illustrated a hydraulic control system embodying the principles of the present invention.
  • a hydraulic circuit generally indicated by the numeral 10, having a pilot operated directional control valve generally indicated by the numeral 12 which is connected in the circuit for directing pressurized fluid from a primary source of high pressure motive fluid such as a supply pump 14 to a hydraulic motor such as a reversible rotary motor 16.
  • a primary source of high pressure motive fluid such as a supply pump 14
  • a hydraulic motor such as a reversible rotary motor 16.
  • the system is designed to control torque control problems associated with rotary hydraulic motors, it is that it will function for load control in linear hydraulic motors.
  • the pump 14 is connected by conduit means in the usual manner for drawing fluid from a sump 18 and supplying it by a main supply line or conduit 20 to the directional control valve 12 which in turn selectively directs the pressure by way of high pressure motor lines 22 and 24 to the reversible hydraulic motor 16.
  • Suitable relief valves 26 and 28 and makeup valves 30 and 32 are provided between the high pressure motor lines 22, 24 and suitable low pressure return passages or lines 34 and 36.
  • the return passages 34 and 36 are in communication by way of a low pressure return passage 38 with a return line 40 to tank or sump 18.
  • a single load check 42 controls a branched supply line or passage 44 which directs fluid from the inlet to the respective motor control lines.
  • a suitable manually operable pilot control valve 46 is connected within a pilot control circuit for directing pilot fluid from an independent pilot pump 48 via pilot control lines 50 and 52 to suitable piston means at the opposite ends of the main control valve for selectively shifting the valve to either one of a fluid directing position from its neutral position as shown.
  • pilot fluid is independent from the source of primary motive fluid. The importance of this will be appreciated from the description of operation on the diagram of FIG. 3.
  • the main control valve 12 comprises a housing 54, having an elongated bore 56 formed therein and a pair of end caps 55 and 57 covering the ends of the bore.
  • the bore 56 is in communication respectively, as illustrated, with the inlet line 20, the motor control lines 22,24 and the return lines 34, 36 and 38.
  • a valve spool 58 is reciprocably mounted within the bore 56 and is operative upon shifting in either direction from the neutral position shown to selectively provide communication between either the inlet or supply conduit 20 and a respective one of the motor control lines 22 and 24 and the other motor control line and low pressure return lines 38 and 40 respectively.
  • the valve spool 58 is provided with the usual annular grooves 60, 62, 64 and 66 which are operative to provide the communication between the respective passages in the valve body. Intermediate the grooves are formed the usual lands which are effective to block the bore between the respective annular passage means at the communication of the various inlet and outlet passageways with the bore.
  • pilot fluid is directed by way of pilot control valve 46 to either end of the valve spool 58, that is, to either the chambers 72 or 74, and for acting on the respective piston means 68 or 70 for shifting the valve spool 58 in a direction away from the respective pressurized chamber.
  • Centering means 76 of a novel construction, to be described, is provided at each end of the spool to bias the spool to its neutral position as shown. While in the neutral position, fluid flowing into the bore 56 by way of supply conduit 20 flows along the spool 58 at grooves 62 and 64 and outward along outlets 38a and 38b to return passage 38 and return line 40 to sump 18. It will be appreciated that instead of connecting the outlets 38a and 38b to the return passage 38, such outlets may be alternately utilized to communicate pressurized fluid to another control valve such as in a bank of valves, not shown.
  • Pressure responsive controlling means are provided to control motor torque in response to operator control position and load pressure.
  • the pressure controlling means of the present invention which is operative in response to pressure in the motor ports or lines to assist in modulating the control valve comprises generally, means such as a pair of pistons 78 and 80 reciprocably disposed in bores 82 and 84 formed in the end caps 55 and 57 at each end of the valve spool 58 and bore 56 and are generally axially thereof.
  • the pistons are operatively connected as by bearing at their inner ends against the ends of the spool 58 and the outer ends thereof define with the respective bores 82 and 84 chambers which are communicated by suitable means such as conduit means 86 and 88 with the respective opposite motor control port.
  • a conduit means 86 communicates the left hand piston 78 and bore 82 with the right hand conduit 24.
  • the conduit 88 communicates fluid pressure in the motor port 22 with the bore 84 where it acts on piston 80.
  • This provides a feedback of motor line pressure for acting on the spool 58 for assisting in controlling the displacement of the spool in proportion to motor line pressure and the pilot control pressure.
  • the motor line pressure will be a direct function of the torque or load on the motor and the pilot pressure will be proportional to the displacement of the pilot control valve 46 and likewise the manual control lever or knob 47 by which it is controlled.
  • the centering means includes a pair of identical assemblies indicated generally at 76 with one at each end of the valve spool comprises zero rate spring centering means acting on each end of the spool 58 to provide a constant force centering means.
  • the zero rate centering means is such that the centering force acting on the spool does not vary with the displacement of the spool but is constant regardless of displacement.
  • the centering means also includes emergency centering means which will also be described hereinafter.
  • the centering means as shown in FIG. 2 comprises a pair of identical assemblies, each of which includes a housing 90 and 92, bores 94 and 96 concentric with bore 56 at each end thereof and secured to caps or housings 55 and 57.
  • the bores 94 and 96 are closed by end caps 98 and 100 having a cylindrical bore for defining pressure chambers 102 and 104.
  • a pair of bores 106, 108 and 110, 112 are formed in the members 55 and 57.
  • Suitable pistons 114, 116, 118 and 120 are reciprocably mounted in the bores and have one end in abutting engagement with the end of spool 58 and the opposite end in communication with pressure chambers 102 and 104.
  • Each of the piston means preferably includes an enlarged head defining annular stop means 122, 124 and 126, 128 respectively for engagement with the housing members 55 and 57 when the spool 58 is in its centered or neutral position.
  • conduit means 106 and 108 communicate fluid from an independent pilot source 48 (i.e. independent of the primary source of motive fluid 14) by way of suitable passage means 110 and 112 in the cap or housing members 55 and 57 for communication with the chamber 102 and 104 of the respective centering means.
  • the pressurized fluid thus introduced into the chambers 102 and 104, acts on pistons 114, 116 and 118, 120 to bias them against the end of piston means 68 and 70 the spool 58 and thus biasing the spool to the right or left toward its centered position.
  • the pilot fluid being of a constant pressure will, therefore, exert a constant pressure on pistons 114, 116, 118 and 120 and thus, a constant pressure for centering the spool 58.
  • the safety or emergency centering means of the present invention comprises plungers or pistons 130 and 132 reciprocably mounted within the bores 94 and 96 and biased by spring means 134 and 136 against the head of pistons 114, 116 and 118, 120 for biasing them toward the end of the spool 58 and thus, the spool 58 to the centered position.
  • the plungers 130 and 132 also define piston means such that pressurized fluid introduced to the chambers 102 and 104 force the piston means or plunger means as illustrated in FIGS. 1 and 2 away from the heads of pistons 114, 116 and 118, 120 to permit fluid operation thereof by the constant force centering means.
  • the springs 134 and 136 will force plungers 130 and 132 against the heads of the piston 114, 116 and 118, 120 and thus, bias the control valve 58 to its centered position.
  • the valve 58 will be automatically returned to its neutral position to shut down the motor 16 should pilot pressure of the system fail.
  • the graph in FIG. 3 illustrates the relationship of motor torque and control lever displacement.
  • Motor torque is plotted vertically as against lever displacement plotted horizontally with zero torque and displacement indicated at point 0 where the vertical and horizontal axis intersect.
  • Motor acceleration is depicted by curve A which intersects line 0-C at point B.
  • pilot pressure for shifting the main control valve spool 58 will begin to build up in chamber 72 or 74.
  • point B (FIG. 3)
  • sufficient pilot pressure will have built up in 72 or 74 to shift spool 58 to a position just beginning to open and communicate primary or working fluid from primary source 14 to motor 16.
  • the spool 58 is shifted further from its neutral position communicating a greater amount of fluid to the motor 16 causing the torque of the motor to increase and the motor to accelerate.
  • the torque on the motor 16 will have a direct relationship to the position of the control lever 47.
  • the main control spool 58 on the other hand will vary in position to maintain a constant torque of the motor.
  • This control arrangement of the present invention provides a system wherein feedback pressure from the motor 16, which feedback pressure is responsive or proportional to the load or torque on the motor 16, will act against the spool 58 by means of pistons 78 and 80 tending to move it to a position reducing the fluid pressure to the motor 16 to maintain a substantially constant torque on the motor for a given control lever setting.
  • the pilot control means shifts the main control valve spool 58 in the usual manner such that, should the operator decide to shift the valve 58 to the right to provide communication between inlet or supply conduit 20 via conduit 44 to the motor control line 22, such communication between conduit 44 and 22 are established by the annular groove 60 when spool 58 is shifted to the right.
  • Such shifting occurs when pilot pressure line 50 is communicated with pump 48 to introduce pressurized pilot fluid into chamber 72 wherein the fluid acts on piston face 68 to shift the spool to the right against the force of the centering means.
  • Pressurization of fluid from the main supply pump 14 to motor control line 22 also communicates that fluid via conduit 88 to piston 80 which acts on spool 58 at the right hand thereof for providing a force opposing shifting of the spool to the right.
  • Opposition to movement of stem 58 is always provided by the forces from both the load piston 80 and the centering pistons 118 and 120 on the right end of the valve when applying pilot pressure to the left end of the stem.
  • the pressure in the motor line 22 will vary with the load on motor 16.
  • the pilot pressure is from an independent source and thus, remain substantially constantly independent of the load on the system.
  • the pilot pressure is generally of lower pressure than that of the working pressure in the system as was supplied from pump 14.
  • the pistons which are responsive to the pilot pressure are larger in diameter than those which are subject to the working pressure of the working system.
  • the relationship of the size of the compensator pistons to those of the pilot control pistons is such that when very high working pressures are present in the working system, the pressure controlling means will be effective to act in opposition to the pilot pressure acting for shifting of the valve spool 58 from neutral to its open position.
  • a modulation of the working fluid by the main control valve will occur in proportion to the pressure in the working system.
  • the system will accordingly modulate the flow of fluid across valve spool 58 of the main working system automatically and overcome or reduce any tendency for rapid acceleration of the motor.
  • the system will function to maintain a substantially constant torque on the motor regardless of the speed of the motor.
  • the constant force centering means as pointed out above will insure that the force necessary to move the spool a given distance as determined by the centering means will be constant throughout the entire range of movement of the spool.
  • the response of the spool to the pressure controlling system will be immediate and directly proportional to the load on the motor as determined by the pressure in the motor control line.
  • valve spool and its controlling system works in the same manner when shifting for reverse drive of the motor 16.
  • the valve spool and compensator can be adapted for use with any type of hydraulic motor.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
US05/594,392 1975-07-09 1975-07-09 Pressure controlled swing valve with safety feature Expired - Lifetime US4041983A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US05/594,392 US4041983A (en) 1975-07-09 1975-07-09 Pressure controlled swing valve with safety feature
CA246,361A CA1030041A (en) 1975-07-09 1976-02-23 Pressure controlled swing valve with safety feature
DE19762617549 DE2617549A1 (de) 1975-07-09 1976-04-22 Druckgesteuertes ventil
FR7614093A FR2317578A1 (fr) 1975-07-09 1976-05-11 Soupape de commande comportant un systeme de securite
BE1007454A BE843052A (nl) 1975-07-09 1976-06-17 Soupape de commande comportant un systeme de securite
JP51071265A JPS529123A (en) 1975-07-09 1976-06-18 Pressure control pilot actuating control valve with safety device
BR7604297A BR7604297A (pt) 1975-07-09 1976-06-30 Valvula de controle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US05/594,392 US4041983A (en) 1975-07-09 1975-07-09 Pressure controlled swing valve with safety feature

Publications (1)

Publication Number Publication Date
US4041983A true US4041983A (en) 1977-08-16

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ID=24378681

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/594,392 Expired - Lifetime US4041983A (en) 1975-07-09 1975-07-09 Pressure controlled swing valve with safety feature

Country Status (7)

Country Link
US (1) US4041983A (ja)
JP (1) JPS529123A (ja)
BE (1) BE843052A (ja)
BR (1) BR7604297A (ja)
CA (1) CA1030041A (ja)
DE (1) DE2617549A1 (ja)
FR (1) FR2317578A1 (ja)

Cited By (32)

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US4185660A (en) * 1978-02-21 1980-01-29 Consolidation Coal Company Directional control valve
US4274443A (en) * 1978-02-21 1981-06-23 Consolidation Coal Company Directional control valve
WO1982002230A1 (en) * 1980-12-24 1982-07-08 Hall Lowell R System with constant force actuator
US4354527A (en) * 1980-10-09 1982-10-19 Caterpillar Tractor Co. Control system for pilot operated valve
US4372193A (en) * 1980-12-24 1983-02-08 Caterpillar Tractor Co. System with constant force actuator
US4463819A (en) * 1981-09-14 1984-08-07 Deere & Company Hydraulic control valve
US4481770A (en) * 1982-03-22 1984-11-13 Caterpillar Tractor Co. Fluid system with flow compensated torque control
US4543875A (en) * 1982-12-07 1985-10-01 Mannesmann Rexroth Gmbh Electro-hydraulic directional control valve
US4665699A (en) * 1981-11-24 1987-05-19 Linde Aktiengesellschaft Hydrostatic drives
US4747576A (en) * 1982-11-04 1988-05-31 Toshiba Kikai Kabushiki Kaisha Flow control valve
US4848404A (en) * 1987-02-18 1989-07-18 Doyle Hickok Hydraulic valve
US4883091A (en) * 1988-12-27 1989-11-28 Ross Operating Valve Company Multi-port self-regulating proportional pressure control valve
US5097745A (en) * 1989-06-20 1992-03-24 Liebherr-Aero-Technik Gmbh Speed control valve for a hydraulic motor speed controlled by pressure between throttle and motor
US5197516A (en) * 1992-05-01 1993-03-30 Moog Controls, Inc. Hydraulic servo valve with controlled disengagement feature
US5316044A (en) * 1992-12-07 1994-05-31 Caterpillar Inc. Hydraulic control valve having a centering spring device
US5609088A (en) * 1994-07-25 1997-03-11 Daewoo Heavy Industries, Ltd. Hydraulic control system for excavations with an improved flow control valve
US5732678A (en) * 1993-06-04 1998-03-31 Man B&W Diesel A/S Slide valve and a large two-stroke internal combustion engine
US5797294A (en) * 1994-06-16 1998-08-25 Zf Friedrichshafen Ag Shift valve
US5829396A (en) * 1996-07-16 1998-11-03 Sturman Industries Hydraulically controlled intake/exhaust valve
US6109162A (en) * 1998-12-02 2000-08-29 Teijin Seiki Co., Ltd. Control valve system
US6167909B1 (en) * 1999-09-28 2001-01-02 Tactair Fluid Controls, Inc. Corrosion and contaminant resistant slide valve
US20030015155A1 (en) * 2000-12-04 2003-01-23 Turner Christopher Wayne Hydraulic valve actuation systems and methods
US20030089407A1 (en) * 2001-08-03 2003-05-15 Bento Jose C. Solenoid valve for reduced energy consumption
US20030140975A1 (en) * 2001-08-03 2003-07-31 Bento Jose C. Solenoid valve for reduced energy consumption
US20060218916A1 (en) * 2005-03-31 2006-10-05 Nabtesco Corporation Driving motor controlling device of construction machine
JP2006283854A (ja) * 2005-03-31 2006-10-19 Nabtesco Corp 建設機械の走行モータ制御装置
US20090294709A1 (en) * 2008-06-02 2009-12-03 Stretch Dale A Two step valve actuator
CN102889397A (zh) * 2011-07-22 2013-01-23 Smc株式会社 节能阀
US11092172B2 (en) * 2019-07-12 2021-08-17 Dennis Keith Reust Seismic vibrator servo valve with proportional linear pressure feedback
US20230175533A1 (en) * 2021-12-08 2023-06-08 Team Industries, Inc. Fixed displacement hydraulic pump match flow demand control system
US20240035493A1 (en) * 2022-07-27 2024-02-01 Liebherr-Aerospace Lindenberg Gmbh Valve and aircraft
US20250109755A1 (en) * 2023-10-03 2025-04-03 Hamilton Sundstrand Corporation (HSC) Valve systems

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US4407122A (en) * 1981-05-18 1983-10-04 Vickers, Incorporated Power transmission
JPS62190173U (ja) * 1986-05-24 1987-12-03
SE458704B (sv) * 1987-05-18 1989-04-24 Atlas Copco Ab Anordning vid ett hydrauliskt drivsystem anslutet till en lastdrivande hydraulmotor
DE4102203A1 (de) * 1991-01-25 1992-07-30 Linde Ag Hydraulisches antriebssystem

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US2157240A (en) * 1935-02-21 1939-05-09 Ex Cell O Corp Valve structure
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US3818802A (en) * 1972-04-27 1974-06-25 Us Navy Speed control mechanism
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US2863423A (en) * 1956-04-11 1958-12-09 Mipsa Sa Hydraulic control installations for machine tools and operating means therefor
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US2157240A (en) * 1935-02-21 1939-05-09 Ex Cell O Corp Valve structure
US2931389A (en) * 1956-04-18 1960-04-05 Moog Servocontrols Inc Servo valve producing output differential pressure independent of flow rate
US2964059A (en) * 1959-03-05 1960-12-13 Moog Valve Co Inc Pressure-flow servo valve
US3267965A (en) * 1963-03-28 1966-08-23 Airmatic Valve Inc Pilot operated spool valve
US3511276A (en) * 1968-04-04 1970-05-12 Caterpillar Tractor Co Fluid control valve with conditional self-actuating means
US3650286A (en) * 1970-05-13 1972-03-21 Us Federal Aviation Admin Hydraulic selector valve
US3640146A (en) * 1970-05-28 1972-02-08 Caterpillar Tractor Co Hydraulic safety override valve
US3746401A (en) * 1971-04-27 1973-07-17 Wagner Electric Corp Control valve and system
US3818802A (en) * 1972-04-27 1974-06-25 Us Navy Speed control mechanism
US3859791A (en) * 1973-07-09 1975-01-14 American Standard Inc Fluid operated hydraulically lapped control apparatus

Cited By (45)

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Also Published As

Publication number Publication date
BE843052A (nl) 1976-12-17
CA1030041A (en) 1978-04-25
FR2317578A1 (fr) 1977-02-04
DE2617549A1 (de) 1977-01-27
BR7604297A (pt) 1977-04-05
JPS529123A (en) 1977-01-24

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